Multiple pump



y 1940- w. H. ROBERTSON MULTIPLE PUMP Filed May 29, 1955 4 Sheets-Sheet l IN VEN TOR IM-Mm a viwfimm lulhln July 16, 1940- w. H. ROBERTSON MULTIPLE PUMP Filed May'29, 1935 4 Sheets-Sheet 2 lllllll /N VEN TOR mzam 1 4 mm July 16, 1940. w RQBERTSQN 2,208,055

MULTIPLE PUMP Filed May 29, 1935 4 Sheets-S11E81. 3

Fzg 5 'INVENTOR y 15, 1940- w. H. ROBERTSON 2,208,055

MULTIPLE PUMP Filed May 29, 1935 4 Sheets-Sheet 4 iii] itlili INVENTOR patented July is, 1940 OFFECE 20 Claims.

This invention relates in general to fluid or liquid dispensing devices and more particularly to a system and apparatus for multiple pumping and feeding of fiuids or liquids and is especially 5 useful in lubricating machinery and vehicles in which there are many bearings requiring continuous supply of lubricant.

This invention has for one of its objects to provide a novel system of lubrication in which pumps H) are collectively operable but individually capable of automatically and positively pumping lubri eating oil from one or more sources of supply to a plurality of places or bearings respectively in the apparatus to which the system. is applied thru individual paths.

This invention has for a further object the provision of a device in which a gang of pumps of the same or diiierent capacities are so constructed and arranged as to be collectively operable in fixed unison for automatically and positively pumping fluids or liquids along individual or independent paths.

Another object of my invention is to provide in a device of this character a driving means for actuating the pistons of said pumps at periodic intervals whose frequency depends on the speed of the machine to which the driving means is connected.

Another object of my invention is to provide no a device of this character that is extremely simple in design, relatively inexpensive to manufacture and easy to build to a variety of specifications calling for various combinations of the number of pumps and the quantities of fluids to 3., be delivered by said pumps respectively.

A further object of this invention is to provide a device in which a gang of pumps of the valveless type have pairs of opposing pistons arranged and connected to produce opposing groups of pistons that are in turn connected to a driving mechanism. in such a manner that one group or units of pistons is actuated independently of a corresponding opposing group or unit of pistons during one interval of actuation, and in unison therewith during another interval, in sequence and in timed relation.

A further object of my invention is to provide a device of this character in which one or more of said pumps serves or serve to supply fluid from a source of supply to others of said pumps through a reservoir and in quantities greater than that released therefrom by said other pumps whereby to establish in said reservoir a high pressure fluid supply.

5 A further object of my invention is to provide in combination with a device of this character a main source of supply and a secondary source of supply that are connected to said pumps in such a manner that the fluid released from said secondary source by the pumps dependent there- 5 on for their supply is replenished therein in greater quantities by the pump or pumps dependent upon the main source for its or their supply, said sources being connected to each other thru a pressure relief means to prevent excessive pressures in said secondary source of supply.

A device constructed in accordance with my invention and incorporated in a lubricating system presents several important advantages. The positive pumping of the liquid in each tube makes 16 possible the use of very small tubes probably not over of an inch outside diameter and therefore a great many tubes could be bound into a cable, similar to a telephone cable. Such a cable could easily be attached to the frame work of 20 a machine and the tubes would branch off from the cable at diiferent points along the cable corresponding to dilferent places needing lubrication, Making use of a group of very small tubes instead of a large tube with branches has the further advantage that the small tube is much more flexible and therefore reducing the possibilities of breakage under vibration. As a further consideration the small tube can be made out of steel or other resilient material or its end can terminate with a steel tube which can be formed into a coil, like a spring, thus permitting the free end to be connected to a bearing that moves relative to the machine frame and hence making possible the automatic lubrication of places that were not so served heretofore. In making use of the valveless type of pump such for example as covered in my copending reissue divisional application Serial No. 745,480, filed March 26, 1935, now He. 20,254, the construction of the pumps is made extremely simple, it requiring merely that a block of metal be formed with as many holes close together as the number of pumps desired to receive the pistons and that only one plate will serve to hold the pistons as a group and transmit motion to them in fixed unison. Furthermore, the valveless pumps being capable of pumping very minute fractions of a drop of oil at a stroke, it will be obvious that a greater number of strokes per hour will be used for pumping a given quantity of liquid than would otherwise be necessary and hence fewer speed reducing gears will be required to get the speed down to the desired frequency. For example, if it were desired to pump one drop of oil per hour the conventional type of pump having two valves probably might be designed small enough to pump one drop per stroke but there would have to be provided a sufficient number of reducing gears to insure that this stroke would occur only one time per hour. However, the valveless pump can easily be designed to pump only ,4 of a drop of oil per stroke and do it accurately and reliably. Hence, its drive shaft needs by comparison only of the speed reduction and consequently fewer reducing gears. Each single pump in a group works on the principle of two opposed pistons separating within a cylinder adjacent an opening and thereby sucking in oil. The pistons then move in constant spaced relation to another opening in the side of the cylinder. The pistons then come closer together and squeeze out the oil. They then move in constant spaced relation back to the first position. Since there are no valves for the fluid to back-wash by in closing, metering of the fluid is extremely accurate for both minute amounts or large amounts depending on size of pistons and lengthof stroke distance.

The speed of travel of the pistons during the periodic actuations thereof is very important, for, if the pistons move too fast inertia resistance of the liquid in the tubes will be added to the normal pressure in the pumps respectively causing the liquid to leak past the pistons, also, on the other hand, if the pistons move too slowly, more time will be afforded the normal pressure to cause the liquid to leak past the pistons thus requiring for either condition a more accurate fit of the pistons and consequently enhancing the manufacturing costs.

Using a train of. Geneva gears simply by themselves would actuate the pistons periodically to any desired frequency depending on the number of gears in the train, but the speed of movement of the pistons would be the same as the driving means for the train gear because when the last gear of such a train finally moved it would have approximately the same speed as the first gear for they would move simultaneously. Hence, if the speed of the driving means is too great or too slow, the speed of the pistons will likewise be too great or too slow. A suitable speed is rendered possible by the use of spur gears and Geneva gears in combination to transmit power from the prime mover to the pistons.

Other and further objects and advantages of the invention will be hereinafter set forth.

In the drawings wherein like reference characters denote likeor corresponding parts,

Fig. 1 is a front elevational view of a novel multi-cylinder pump device in a fluid feed system embodying my invention.

Fig. 2 is a side elevational view of the device shown in Fig. 1 looking from right to left and showing a fluid receptor with portions broken away and in section and a fluid transmission cable having one of its fluid transmission lines connecting the receptor to the fluid pump device.

Fig. 3 is an enlarged sectional view taken on the line 33 of Fig. 2.

Fig. 4 is a View of one of two like cams provided with races on opposite sides thereof for controlling the cycle of operation of the pump pistons.

Fig. 5 is a sectional view on the line 5-5 of Fig. 3.

Fig. 6 is a sectional detail view taken on the line 66 of Fig. 3..

Fig. 7 is an elevational view showing a detail assembly of the connections for actuating the pistons with the cylinder blocks and fractional portion of frame shown in phantom.

Figs. 8 to 16 are detail views of different parts shown in Fig. 7, and 7 Figs. 1'7, 18, 19 and 20 are views partly in section and partly in elevation showing stages of operation that are characteristic of all the pumps, and

Fig. 21 is a view of a further embodiment of my invention.

The multi-pump device illustrated herein as constituting a part of a system for automatically lubricating the various bearings of an automobile or the like, is adapted to be operated by power taken from the prime mover or motor through any suitable power take-oil device such as a belt l2 connecting a pulley (not shown) on the engine drive shaft and a pulley M fixed to and mounted on a driving shaft iii of the multi-piston driving mechanism that is supported by and housed within the casing or framework [8. Fluid is transmitted from the respective outlets of the multi-pump device to the various bearings of the automobile through individual transmission lines or pipes l9 that are grouped together and connected at convenient points along the chassis framework by means of housing plates 2!. As illustrated in Fig. 2, the housing plate N is provided with an opening 23 to permit the branching 01f of one of the transmission lines I? for connection with its corresponding bearing 2!. The bearing 2i forms part of a spring suspension shackle 23 that is capable of vibrating relative to the frame. Lubrication of the same and similar mounted bearings of the vehicle is made possible by making the tube preferably from steel and forming the branched-01f portion thereof into a helical spring coil 25, the lower end 21 of which is detachably connected by means of a suitable fitting 28 to a nipple 3! of well known construction for effecting communication with the bearing 2|.

The driving mechanism as illustrated herein and as shown in Figs. 3,4, 5 and 6, comprises a train of speed reduction gearing operating continuously and a train of speed reduction gearing operating intermittently that are combined and connected between the driving shaft 58 and a pair of spaced cams 26!, 22 for actuating said cams periodically a definite part of a revolution at a predetermined frequency and at a predetermined rate of speed.

The continuous reduction or compound gearing consists of a worm 2d a driven wormwheel 25 meshing therewith and a train of four spur gears 28, 30, 32 and. 36 arranged in pairs of large and small gears on parallel shafts 33, 38 so that they intermesh; the shafts 36, 38 being journaled in the casing 98. Whereas the first driving spur gear 28 is fixedly connected to the wormwheel 26 and is rotatable therewith about the shaft 35 and the second driven spur gear 3-; is connected to and rotates with the first driver of the intermittent reduction gearing, the first driven gear 30 and second driving gear 32 are connected together and rotate about the shaft 38. Motion is thus transmitted from the shaft E6 to the driven gear 34 at a predetermined velocity ratio and the direction of motion of the driven gear 34 is in the same sense as that of the worm wheel 25.

The intermittent speed reduction gearing consists of a compound arrangement in which two sets of Geneva stops are interconnected through a continuous drive. One Geneva stop is connected to and driven directly by the spur gear 33 and the other Geneva stop is connected to and drives the cams 20, 22. The drivers 40, 42 of said Geneva stops rotate about shaft 36 whereas the followers 44, 46 are mounted on but rotate the shaft 38, the former rotating at times about and at times with the shaft 38 and the latter rotating at all times with said shaft. Said drivers 40, 42 are provided with studs 48, 50 respectively that periodically engage with the six radial slots 52 formed in each of the corresponding followers 44, 46, which have attached thereto locking plates 58, 60, each being formed with six concave surfaces 62 of such curvature as just to fit the peripheral edge of the complementary locking plates 64, 86. The locking plates 58, 60 have their respective concave surfaces arranged between radial slots of'the followers 44, 46 and the locking plates 64, 66 are cut away at 61 to allow their respective followers to make a one-sixth turn after which said plates look their complementary followers stationary while the driver of each Geneva stop makes the remaining fixe-sixths of its revolution. Thus the drivers 40, 42 make six revolutions each to give their respective followers 44, 46 one complete turn.

In order to obtain a continuous connection between the driven member or follower 44 of the first Geneva stop and the driving member 42 of the second Geneva stop a plate 68 having six radial slots 10 is attached to the follower 44 and the driver 42 is provided with six studs 12.

The slots 10 are so arranged with respect to the stud I2 that as one stud leaves its corresponding slot the following stud enters the following slot. It will be obvious that in place of the plate 68 and the stud 12 there could be substituted a driving spur and a driven spur gear to produce the continuity of drive between the first driven part and first driving part of the Geneva stops.

In operation the worm 24 turns the worm gear 26 which in turn drives the freely rotating gear 30 through the pinion 28. The gear 30 drives the gear 34 through the pinion 32. The plate 40 being fixed to the gear 34 will drive the follower 44 through a single stud 48 one-sixth of a revolution for every complete revolution of the plate 40, the plate 44 being locked by the plates 58 and 64 when not actuated. The driving plate 68 is driven by the follower 44 and in turn drives member 42 thru the six studs on member 42 and six slots on plate 68. Member 42' in turn through stud 50 drives the follower 46 one-sixth of a revolution for every complete revolution of member 42. The follower 46 drives the cam 20 through a clutch connection 1618.

A material saving in the cost of manufacture may be accomplished by making the several parts of the continuous and intermittent trains of gearings by stamping operations rather than machining operations.

A positive driving connection between the cams 20, 22 that are fixedly connected by pins 14, 14 to opposite ends of shaft 38 and the intermittent train is obtained by means of a tooth clutch one part I6 of which is made integral with the locking plate 60 and the other part 18 of which is made integral with the cam 20. These cams are formed with grooves or races 80, 82 of different curvatures on the opposite faces of each. The inwardly presenting grooves 80, have the same curvature and control the verticle movements of an inner pair of driving pitmans or driving rods 84, 86 through rollers 88, 88 attached thereto. The outwardly presenting grooves 82, 82 likewise have the same curvature and control the verticle move-- ments of an outer pair of pitmans or driving rods 90, 92 through rollers 94, 94 attached thereto. The inner and outer pairs of driving rods have a width at their respective upper and lower ends (see Fig. 5) that is approximately equal to the distance between the walls 9|, 93 which therefore serve as guides to prevent edgewise movement thereof. The curvature of the cam races are such as to cause the pistons to be moved in the sequence shown for one pair of pistons in Figures 17 to 20. Starting with Fig. 20 the pistons are moved closer together to squeeze out the fluid and then occupy the position shown in Fig. 17. Thereafter they are moved in constant spaced relation until they arrive at the position shown in Fig. 18. At this point in the cycle they are separated to suck in fluid as shown in Fig. 19 and then they are moved in constant spaced relation to the position shown in Fig. 20 with the fluid trapped between them. The cycle of the operation is now completed. The relation of the cam surface or groove with respect to the intermittent gears or Geneva gears and the plungers is such that the suction and compression movements, respectively, occur periodically and each movement is completed in one interval corresponding to the time that the cams 20, 22 are rotated one step by the Geneva gearing and as illustrated of a revolution of the cam.

The inner pair of driving rods 84, 86 are further guided against lateral movement by the portions 96, 98 struck up from the side walls 9|, 93 of the casing at the lower ends thereof. Likewise the driving rod 90 is also guided against lateral movement by the struck up portions 98 and stud 99 while the outer driving rod 92 is guided against such lateral movement by the cam 20 and side wall 95.

Referring to Figs. '7 to 10 it will be seen that each of the inner driving rods is composed of two links, an upper link I00 and a lower link I02. The pair of lower links I 02, I02 are arranged between the upper links I00, I00 and connected thereto by means of pins I04, I04. Spacers I06, I08, I I0 are mounted on each of the pins between the corresponding lower and upper links and between the lower links for respectively obtaining the desired spaced relation therebetween.

The inner pair of driving rods 84, are respectively connected by means of cross members H2, H2 to series arranged groups A, A of correspondingly arranged pistons a, a, a that are respectively disposed at the bottom of and extend upwardly in working relation within the cylinders c, c, c of blocks H4, II4, that are in turn disposed within and supported by the casing or frame work I8 and likewise the outer pair of driving rods 90, 92 are connected by cross members H6, H6 to two series arranged groups B, B

of pistons b, b, b that are arranged in opposition respectively to the first two mentioned groups.

Each cylinder block I I4, the opposing groups of pistons arranged in working relation with cylinders thereof and the upper and lower cross members H6, H2 supporting the piston groups a, a, a and b, b, b constitute an assembly unit. Since these unit assemblies are alike in construction a description of one will sufiice for both. The upper and lower piston or plunger supporting cross-members H6, H2 are similar in construction and are similarly connected to their respective driving rods by means of tongues I20, II8 respectively at the opposite ends of each cross member interfitting with corresponding recesses I24, I22 formed in said driving rods; the tongues II8 of the lower cross member engaging with the recesses I22 and the tongues I of the upper crossmember engaging with the recess I24.

The upper cross member is required to be of greater length than the lower cross member be-- cause of the greater spacing between the outer connecting rods. Also in order to permit the lower cross-member to be connected to the inner connecting rods, the upper cross-member IIB that is disposed between the lower cross-members H2, IIZ is provided with recesses I26, I28. It is not necessary that the other upper cross member be provided with such recess since the links I00, I00 do not extend therethrough. However, an interchangeability of parts is made possible by so doing and also a saving in the cost of manufacture is effected by using the same stamping die for both parts. By forming the links I00, I00 with cut away portions I on opposite sides thereof and by providing sufficient clearance between the higher positioned of the two upper cross members and the upper ends of said links, that are shaped in form of ears I32, I32, the two pairs of inner and outer connecting rods are permitted unrestrained verticle movement that is imparted thereto by the cams 20, 22.

While the opposing pairs of plungers or pistons may be of the same or different diameters corresponding to the diameters of their respective cylinders or bores formed in the cylinder blocks, their connecting ends as well as the complementary connecting means constituting a part of the cross members are identical in construction.

It will be seen that each plunger as shown in Fig. 15 is formed at its connecting end with a pair of spaced integral portions or flanges I34, I36, the outer flange I34 of which is capable of being passed thru an enlarged portion I38 of a corresponding opening of the openings I40 formed in its supporting cross member. The connecting end of the plunger is also formed with a reduced portion I42 that is moved laterally into and maintained within a restricted or narrowed portion I44 of the openings I III by spacer means, such as a corresponding spacer portion of the portions I46 provided between the openings I41 formed in a locking plate I48 that is adapted to receive the outer flange I34 when the plunger is arranged within the restricted portion I44. Thus it will be seen that the flanges I34, I36 and reduced portion 142 of each plunger cooperate with the opposite faces I50, I52 of respective supporting members and with the sides of the restricted portions I44 of the openings I40 thereof together with the spacer portions I46 to prevent relative verticle and lateral movements therebetween and provide .a comparatively rigid connection.

The upper and lower locking plates I48, I49 have the same configuration as the piston supporting plates to which they are respectively connected, so that by making the openings I22, I24 formed in the driving rods of suitable size to receive the tongues I I9, I2I respectively in addition to the corresponding tongues of the piston supporting members, the locking plates will be maintained connected with the supporting members in the proper position to lock the piston end to the supporting plates.

The cylinder block is preferably made from a piece of solid metal that is square along its sides I54 and ends I55 so as to provide flush engagement with the walls of the casing. The ends of the block are in the form of narrow projections that are received within and in spaced relation to the sides of the openings I 50, I of the inner and outer pairs of driving rods to permit unrestricted cam operated movements thereof. The cylinder block is provided with two parallel rows of bores that serve as working cylinders for different pairs of opposing pistons. Each cylinder has a separate'inlet Hi2 formed by boring transversely through the cylinder bore and sealing one end of the bore by a Glosely fitting plug made of a suitable fibrous vmaterial, and a separate outlet I64 and the inlets of one row of cylinders are in communication with a conduit I68 whereas the inlets of the other row of cylinders are in communication with a further and separate conduit I68. These outlets and conduits are also .formed in the cylinder block by boring operations. Each of the cylinder blocks is supported within the casing in the same manner. As illustrated the cylinder block is attached at its opposite side faces to the side walls 9|, 93 by means of nipples I 70 for the outlets of each row of cylinders, the nipples passing through openings in these wallsand being engaged with threaded counter bores in the cylinder block, and the cylinder block is also attached at its opposite ends I58 to its corresponding walls by means of screws I72 that pass through openings in the walls and threadedly engage with the cylinder block.

A pair of supply conduits I'M-establish communication between the rows of cylinders of the lower cylinder block and two separate sources of supply such as tanks I10, I18. Likewise a pair of supply conduits I30 connect the separate tanks I82, I 84 to the rows of cylinders of the upper cylinder.

Where the same grade of lubricant is intended to be used for all the different bearings a single tank or source of supply such as the crank case of an engine would serve all the pumps, otherwise difierent tanks are used for different grades of lubricant.

In order to facilitate the removal or assembly of each cylinder block together with the opposing groups of pistons and their respective supporting and locking members, the driving rod is made of two parts, an upper link I86 and a lower link I88 that are detachably connected together by means of pins I90 riveted to the lower link and received within openings formed in the upper link. Also the .side wall 9i is made of an upper plate cover I92 and a lower plate I04, the upper plate being readily detachably connected to the casing by suitable threaded members. By

making the opening covered by the plate I92 of sufficient size, each cylinder block the groups of pistons and. the upper .and lower supporting and locking plate members can be'inse'rted endwise therethrough as unitary assemblies.

After the insertion of these assemblies and their attachment to the driving rods 86, 92 disposed on the opposite side of the opening, the links I00, I86 are inserted through the openings and connected to the assemblies inthe manner indicated above and to their respective lower link members I02, I88. The cover plate I92 is then attached to the upper and lower positioned cylinder blocks by nipple I10 and threaded member I12 respectively and to the top wall I94 of the casing by suitable means such as threaded members- I96.

A further embodiment. of my invention is shown in Fig. 21 in which the various parts of the above described embodiment and the arrangements thereof are identical except that one pump of each of the groups of pumps is separated from the remainder and serves to supply lubricant from a main tank 2m: to an auxiliary tank 202 and maintains the same therein at a higher pressure by reason of the fact that the auxiliary tank 202 is sealed and because the pumping capacity of the segregated pump is greater than the total capacity of all the remaining pumps of the group. For this purpose the cylinder block (not shown) is formed with abore 204 (shown dotted) that constitutes with the pipe 206 an inlet path for the lubricant pumped by said segregated pump, the pipe 206 and cylinder block being connected together by means of a nipple 208 through the wall of the casing. The outlet of the pump is communicatively connected to the tank 2% through a pipe 2H) that is connected at its upper end to the outlet of the segregated pump by means of a nipple ZIZ in a manner already described above. This outlet is formed at the other end with two branches M4, 286, the branch 21 i extending into the tank 202 and having normally open communication therewith, while the branch H6 is connected to the tank 266 and is normally shut ofi therefrom by means of a pressure relief valve ZIB. The desired pressure in the tank 292 is determined by adjusting the tension of spring 220 through adjusting nut 222. Thus when the pressure in tank 202 exceeds that for which it is adjusted the relief valve is opened by reason of the back pressure of liquid in the tank 202 and pipe 2 l4 and thereafter and as long as the pressure in tank is maintained excessive, the lubricant pumped by the segregated pump is caused to circulate from the tank 200 through pipe 206 through said segregated pump thence through pipe 21!] and finally back to the tank 2% through the valve.

The expression gearing operating intermittently or intermittent gearing as used herein is meant to describe a mechanism in which a driving member, during each revolution thereof, moves by direct contact a driven member through part of a revolution, there being one or more periods of rest for the driven member before it is turned completely around or through one revolution. Such mechanism is intended to include, in addition to the intermittent gearing, illustrated herein, other equivalent gearing of this character and will be termed in the claims as Geneva type.

I desire that my invention be regarded as limited only by the appended claims, inasmuch as many modifications and variations within the spirit of my invention will be found possible and desirable in adapting its various novel features for other uses than in automobiles.

What I claim and desire to secure by Letters Patent is:

1. In a multi-cylinder pump device, the combination with a supporting case provided with an opening and a driving mechanism supported by said casing of an assembly comprising a group of working cylinders detachably connected to said casing, pistons working therein, and means connecting said pistons to operate in unison and being detachably connected to said driving mechanism, said assembly being so constructed and arranged as to be capable of being inserted through said opening for efiecting detachable engagement of said group of cylinders and said pistons to said casing and driving mechanism respectively.

2. A-fluid pump device comprising, a workingcylinder-group, each cylinder being provided with an inlet and an outlet and having a pair of pistons working therein, means connecting the correspondingly arranged pistons of said pairs of pistons in separate units and means for intermittently actuating said units including an operating cam for each unit, said units working independently during one interval of actuation and in unison during another interval, in sequence and in time-spaced relation between. movements to receive the fluid from said inlets between the opposed faces of respective pairs of pistons, to translate the same and to subsequently discharge the same through corresponding outlets.

3. Means for detachably connecting a plurality of pistons to be operated as a unit comprising, in combination, a supporting plate having a plurality of enlarged openings with slots at one end thereof respectively, a corresponding plurality of pistons, each piston beingprovided with a head adapted to extend through an enlarged opening and with a reduced portion for complemental engagement with the corresponding slot and means for detachable engagement with the head of said pistons to maintain said pistons operatively connected with said supporting plate.

4. A lubricating system comprising, a plurality of valveless. pumps, each pump having a working cylinder provided with an inlet and an outlet and a pair of working pistons, a lubricant supply conduit in communication with each of said inlets and a plurality of discharge tubes respectively connected to said outlets, means for actuating said pairs of pistons to receive the fluid from said inlets simultaneously between the opposed faces of respective pairs of pistons, to translate the same simultaneously and to subsequently discharge the same simultaneously through corresponding outlets, and a train of intermittent gearing of the Geneva type operatively connected with said first mentioned means for causing the same to operate at a relatively low cyclic frequency but at a speed suitable for obtaining efiicient working of said pistons.

5. A lubricating system comprising, a plurality of valveless pumps, each pump having a working cylinder provided with an inlet and an outlet and a pair of working pistons, a lubricant supply conduit in communication with each of said inlets and a plurality of discharge tubes respectively connected to said outlets, means for actuating said pairs of pistons to receive the fluid from said inlets simultaneously between the opposed faces of respective pairs of pistons, to translate the same simultaneously and to subsequently discharge the same simultaneously through corresponding outlets, a train of intermittent gearing of the Geneva type drivingly connected with said first mentioned means for causing the same to operate at a relatively low cyclic frequency but at a speed suitable for obtaining efficient working of said pistons, and means to prevent movement of said actuating means when said gearing is inoperative.

6. In combination with a pump device having a working cylinder, a piston working therein and means for actuating said-piston through a given operating cycle; of means for driving said piston actuating means at a suitable speed to obtain efiicient piston working and intermittent gearing of the Geneva type operatively connected with said piston actuating means and said driving means to thereby intermittently operate said piston actuating means at a cyclic frequency less than that of said driving means.

means for actuating said piston thru a given operating cycle; of driving means operating said actuating means at a rotary speed sufficient for obtaining efficient piston working, intermittent gearing of the Geneva type operatively connected with said piston actuating means and said driving means for obtaining an intermittent operation of said piston actuating means and means for stopping and locking said actuating means against further movement at the end of each operation thereof.

8. In combination with a pump device having a working cylinder and a piston working therein, means for actuating said piston thru a given operating cycle; of driving means operating said actuating means at a rotary speed suflicient for obtaining efficient piston working and a train of intermittent gearing of the Geneva type oper- )atively connected with said piston actuating means and said driving means, the gears of said intermittent gearing arranged in series driving relation to obtain a relatively low period of cyclic operation of said actuating means.

9. A pump device comprising, in combination, a working cylinder having an inlet and an outlet, a pair of pistons working therein, means for moving said pistons, in timed relation to each other,

thru a given operating cycle, driving means operable at a suitable speed for obtaining efiicient working of said pistons and a train of intermittent gearing of the Geneva type connected in series driving relation between said driving means and said pistons moving means for interj mittently operating said moving means at a relatively low cyclic frequency.

10. A pump device comprising, in combination, a working cylinder having an inlet and an outlet,

a pair of pistons working therein, means for moving said pistons, in timed relation to each other, thru a given operating cycle, driving means operable at asuitable speed for obtaining efficient Working of said pistons and a train of intermittent gearing of the Geneva type operatively connected with said driving means and said pistons moving means for intermittently operating said moving means at a relatively low cyclic frequency.

1 pistons of each pair of pistons to provide a pair of piston-groups, means for moving said pistongroups in timed relation to each other thru a given operating cycle, means for driving said 1 last mentioned means at a speed suitable for obta'ining efficient working of said piston groups and a train ofintermittent gearing of the Geneva type connected in series driving relation between said driving means and said piston-groups moving means for intermittently operating said last mentioned means at a relatively low frequency.

12. In combination with a fluid pump device comprising, a working cylinder having an inlet and an outlet, a pair of pistons working in said cylinder and means positively operatively connected with said pistons for operating the same, in timed relation to each other, thru a given operating cycle of means for driving said last mentioned means at a rotary speed suitable for 3 obtaining efficient working of said pistons including compound spur and intermittent gearing of the Geneva type operatively connected with said pistons actuating means, said gearing serving to obtain a relatively low period of cyclic operation of said actuating means.

actuating means at the end of each intermittent 7 operation.

14. In a combination with a pump device having a cylinder and a piston Working therein and means for actuating said piston thru a given operating cycle; of intermittent gearing of the Geneva type for operating said actuating means, intermittently, at a speed suitable for obtaining efiicient piston Working but at a relatively low cyclic frequency, said means serving further to stop and lock said actuating means against further movement at the end of each operation thereof.

15. In a combination with a pump device having a cylinder and a piston working therein and means for positively actuating said piston thru a given operating cycle; of intermittent gearing of the Geneva type for operating said actuating means, intermittently, at a speed suitable for obtaining efiicient piston working but at a relatively low cyclic frequency, said means serving further to stop and lock said actuating means against further movement at the end of each operation thereof.

16. In a multi-cylinder pump device comprising; in combination, a group of working cylinders, a support for said cylinders, a piston working in each of said cylinders, means for actuating said pistons thru a given operating cycle and means readily detachably connected to said pistons and to said actuating means for causing said pistons to be moved substantially in unison, said detachable means including a plate for supporting said pistons in sliding engagement and means for locking said pistons against displacement.

17. A fluid pump device comprising, in combination, a working-cylinder group, each cylinder being provided with an inlet and an outlet and having a pair of pistons working therein, separate means connecting the correspondingly arranged pistons of. each pair of pistons to provide a pair of piston-groups, means for moving said piston-groups in timed relation to each other thru a given operating cycle, means for driving said last mentioned means at a speed suitable for obtaining efiicient working of said piston groups and intermittent gearing of the Geneva type operatively connected with said driving means and-said piston-groups moving means for intermittently operating said last mentioned means at a relatively low frequency.

1%. A pump device having a working cylinder, a piston working therein, means for actuating said piston thru a given operating cycle and intermittent gearing of the Geneva type operatively associated with said actuating means to thereby effect an intermittent operation oi-said piston.

19. A pump device having a working cylinder, a piston working therein, means for actuating said piston thru a given operating cycle and a train of intermittent gearing of the Geneva type operatively associated with said piston actuating means to effect a relatively low cyclic frequency of operation of said piston actuating means.

20. A pump device having a working cylinder, a piston working therein, means for actuating actuating means to thereby operate said piston 5 intermittently and at a cyclic frequency less than that of said continuous gearing.

WILLIAM H. ROBERTSON. 

